CN113128091B - High-speed railway track modal design method for inhibiting train line coupling resonance - Google Patents
High-speed railway track modal design method for inhibiting train line coupling resonance Download PDFInfo
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Abstract
The invention discloses a high-speed railway track modal design method for inhibiting train line coupling resonance, which comprises the following steps of: calculating a vehicle structure mode and a track structure mode according to the information of the vehicle and the high-speed railway track, and analyzing whether the matching results of the two modes are overlapped; if the overlap occurs, recalculating the rail mode by changing one or more of the rail structure parameters to make the rail structure mode range avoid the vehicle structure mode range; if the vehicle-track rigid-flexible coupling dynamic performance analysis model is not overlapped, a vehicle-track rigid-flexible coupling dynamic performance analysis model is constructed, dynamic simulation analysis is carried out on the constructed vehicle-track rigid-flexible coupling dynamic performance analysis model, whether abnormal vibration caused by resonance exists during vehicle running is judged, if the abnormal vibration exists, track structure parameters are modified until the suppression of the train line coupling resonance is achieved, the method considers the vibration influence of the track structure on the vehicle structure from the resonance angle, and the method has certain guiding significance for the construction or the transformation of the high-speed railway.
Description
Technical Field
The invention belongs to the technical field of rail transit, and particularly relates to a high-speed railway track mode design method for inhibiting train line coupling resonance.
Background
The vehicle-track is used as a large system which is mutually disturbed, the coupling vibration condition of the vehicle structure and the track structure is determined by the integral mode matching degree, and the running stability and the running safety of the vehicle are influenced to a certain degree. In practice, the vehicle structure comprises a vehicle body structure, a suspension structure, a frame structure, a wheel set structure, and the track structure comprises a steel rail structure, a track plate structure. In these many structures, the modal response of each structure is different, so that if the modal matching degree is not good, the vehicle-track resonance occurs, and the vehicle running comfort and even the safety problem are caused. In recent years, with further planning of high-speed railway construction, more and more high-speed railways are constructed and put into use. Therefore, from the viewpoint of the line coupling resonance, it is necessary to design the mode of the track structure to avoid the vehicle-track coupling resonance.
For the problem of resonance, the traditional method is designed aiming at the structural mode of the vehicle, so that the mode matching of the vehicle is good, and the problem of resonance of the vehicle is avoided. And the vehicle-track is taken as a large system which is mutually turbulent, and for the resonance problem, the mode of the track structure should be taken into consideration, so that the mode matching is more reasonable. In addition, for the problem of vehicle-track rigid-flexible coupling resonance, not only the resonance problem of the natural mode but also whether abnormal vibration caused by resonance exists under mutual excitation or not, namely, the mode problem under excitation is considered.
The method for designing the mode of the high-speed railway track structure for inhibiting the train line coupling resonance can ensure that a large system with vehicle-track mutual disturbance can practically and effectively avoid the overlapping area with the vehicle mode from the mode of the track structure, and provides a suggestion in the mode matching aspect which is favorable for the safety and the stability of vehicle operation for the construction of the track structure.
Disclosure of Invention
In order to overcome the defects, the inventor of the invention provides a high-speed railway track mode design method for inhibiting the train line coupling resonance through long-term exploration attempts, multiple experiments and efforts, continuous innovation and innovation, the method can calculate the vehicle structure mode and the track structure mode according to the information of a vehicle and a high-speed railway track, avoid an overlapped area of the track structure mode and the vehicle structure mode by changing the track structure, establish a vehicle-track three-dimensional rigid-flexible coupling dynamic performance analysis model for further ensuring the vehicle running performance, perform dynamic simulation calculation on the coupling model, judge whether abnormal vibration caused by resonance exists during the vehicle running according to the calculation result, and inhibit the resonance again by changing the track structure if the abnormal vibration exists until the train line coupling resonance is successfully inhibited.
In order to achieve the purpose, the invention adopts the technical scheme that: the method for designing the track mode of the high-speed railway for inhibiting the train line coupling resonance comprises the following operations:
s1, calculating a vehicle structure mode and a track structure mode according to information of a vehicle and a high-speed railway track;
s2, analyzing whether the matching results of the vehicle structure mode and the track structure mode are overlapped or not;
s3, if mode matching generates overlapping, recalculating the rail mode by changing one or more of the rail structure parameters to ensure that the rail structure mode range avoids the vehicle structure mode range;
if the mode matching is not overlapped, a vehicle-track rigid-flexible coupling dynamic performance analysis model is constructed, dynamic simulation analysis is carried out on the constructed vehicle-track rigid-flexible coupling dynamic performance analysis model, and whether abnormal vibration caused by resonance exists during the running of the vehicle is judged;
s4, if abnormal vibration exists, returning to the step S3, and re-selecting different track structure parameters to re-calculate the track mode;
if abnormal vibration does not exist, the purpose of inhibiting the coupling resonance of the train line is successfully achieved.
According to the high-speed railway track mode design method for inhibiting train line coupling resonance, a further preferable technical scheme is as follows: and in the S1, the vehicle information comprises vehicle suspension system parameters, vehicle body structure parameters, framework structure parameters and wheel set structure parameters.
According to the high-speed railway track mode design method for inhibiting train line coupling resonance, a further preferable technical scheme is as follows: and S1, the information of the high-speed railway track comprises steel rail structure parameters, track slab structure parameters and fastener parameters.
According to the high-speed railway track mode design method for inhibiting train line coupling resonance, a further preferable technical scheme is as follows: the vehicle structure mode in the S1 comprises a vehicle suspension mode, a vehicle body flexibility mode, a framework flexibility mode and a wheel set flexibility mode, and the track structure mode comprises a steel rail flexibility mode, a track plate flexibility mode and a track integral mode.
According to the high-speed railway track mode design method for inhibiting train line coupling resonance, a further preferable technical scheme is as follows: and S3, the structural parameters of the track comprise the length, the width and the height of the track slab, the rigidity of the track slab and the rigidity of a fastener.
According to the high-speed railway track mode design method for inhibiting train line coupling resonance, a further preferable technical scheme is as follows: and establishing a flexible vehicle body, a flexible framework, a flexible wheel pair and a flexible track in the vehicle-track rigid-flexible coupling power performance analysis model established in the S3.
According to the high-speed railway track mode design method for inhibiting train line coupling resonance, a further preferable technical scheme is as follows: and S3, different track structure parameters are reselected, and the influence factors are unreasonable matching among the track mode, the vehicle distance, the vehicle wheelbase and the vehicle mode.
Compared with the prior art, the technical scheme of the invention has the following advantages/beneficial effects:
1. the model established by the invention is a vehicle-track rigid-flexible coupling model, the flexible vehicle body, the flexible framework, the flexible wheel pair, the flexible steel rail and the flexible track plate are established, and compared with a rigid body hypothesis, the model can enable the modes of the vehicle and the track structure to be more similar to the modes of actual conditions.
2. The vehicle-track is used as a large system which is mutually disturbed, and the mode of the track structure is designed to avoid the coupling resonance of the vehicle-track, so that the mode matching problem is not only limited in the vehicle, but also expanded between the vehicle and the track, and the mode matching consideration is more comprehensive.
3. For the problem of rigid-flexible coupling resonance of the vehicle and the track, not only the resonance problem of the inherent modes of the structures of the vehicle and the track is considered, but also whether abnormal vibration caused by resonance exists under mutual excitation or not is considered.
4. The method for designing the mode of the high-speed railway track structure for inhibiting the train line coupling resonance can provide a suggestion in the mode matching aspect which is favorable for the running safety and the stability of a vehicle for the construction of the track structure from the mode of the track structure for a large system of the vehicle-track mutual coupling disturbance.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
FIG. 1 is a flow chart of a high-speed railway track mode design method for suppressing train line coupling resonance according to the invention.
FIG. 2 is a schematic diagram of a vehicle-track coupling of a high-speed railway track mode design method for suppressing line coupling resonance according to the invention.
FIG. 3 is a flexible track finite element model of the high-speed railway track mode design method for inhibiting train line coupling resonance.
FIG. 4 is a flexible vehicle finite element model of the high-speed railway track mode design method for inhibiting train line coupling resonance.
FIG. 5 shows the flexible car body components and the low-order modal frequencies of the track of the high-speed railway track modal design method for suppressing the train line coupling resonance.
FIG. 6 is a time-course diagram of the lateral acceleration of the car body floor during coupling resonance in the method for designing the track mode of the high-speed railway for inhibiting the coupling resonance of the train line.
FIG. 7 is a time-course diagram of the lateral acceleration of the car body floor under the normal working condition of the high-speed railway track mode design method for inhibiting the train line coupling resonance.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions in the embodiments of the present invention are clearly and completely described below, and it is obvious that the described embodiments are a part of the embodiments of the present invention, not all of the embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without inventive efforts based on the embodiments of the present invention, are within the scope of protection of the present invention. Thus, the detailed description of the embodiments of the present invention provided below is not intended to limit the scope of the invention as claimed, but is merely representative of selected embodiments of the invention.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it may not be further defined and explained in subsequent figures.
Example (b): as shown in fig. 1, a method for designing a mode of a high-speed railway track for suppressing line-coupled resonance includes the following operations:
s1, calculating a vehicle structure mode and a track structure mode according to information of a vehicle and a high-speed railway track;
the high-speed railway track information comprises steel rail structure parameters, track plate structure parameters and fastener parameters.
The vehicle structure mode comprises a vehicle suspension mode, a vehicle body flexibility mode, a framework flexibility mode and a wheel pair flexibility mode;
the track structure mode comprises a steel rail flexible mode, a track plate flexible mode and a track integral mode.
The vehicle suspension mode is determined by suspension stiffness and damping, and the mass properties of the vehicle. The vehicle suspension mode can be obtained by establishing a vibration equation of a vehicle system, and a free motion equation of the vehicle system is shown as the formula (1-1):
in the formula: M-N-order quality matrix of the system;
C-N-order damping square matrix of the system;
K-N-order stiffness matrix of the system;
and X is generalized displacement of the N order.
The characteristic equation of the available vehicle suspension system is shown as the formula (1-2):
|K-ω 2 M|Φ＝0 (1-2)
solving the equation can obtain the natural frequency omega and the natural mode phi of the vehicle. (see, in particular, ni jowar, vibromechanics [ M ]. Department of Sigan university of transportation, 1988.)
The flexible mode of the vehicle-track system is determined by its structural shape and material properties. The structure of the vehicle body, the framework, the wheel pair, the steel rail and the track slab adopts finite element software to establish a finite element model thereof, modal analysis is carried out, and then a modal superposition method is adopted to calculate the flexible vibration of the vehicle body, the framework, the wheel pair, the steel rail and the track slab. The motion equation of the flexible vibration equation of the structure in the floating coordinate system is shown as the equation (1-3):
in the formula:
u f -displacement, velocity, acceleration of flexible vibration of the structure;
M f -a mass matrix of the structure;
C f -a damping matrix of the flexible deformation of the structure;
K f rigid bodies of flexible deformation of structuresA degree matrix;
F f -a load force acting on the structure.
Similarly, the mass matrix M according to the structure f Stiffness matrix K f The characteristic equation of the flexible deformation of the structure can be obtained as shown in the formula (1-4):
|K f -ω i 2 M f |ψ f ＝0 (1-4)
wherein: psi f -a structure flexural vibration natural mode;
ω i -natural frequency of flexible vibration of the structure.
Based on the mode superposition principle, the structure flexible vibration is as shown in the formula (1-5):
in the formula: psi f -a modal matrix of the structure;
q f -a modal coordinate vector of the structure;
Ψ fi -a structural body order i modal vector;
q fi -a structure ith order modal coordinate;
so that its vibration equation can be decoupled into a differential equation associated with its front NM order mode as shown in equations (1-6):
in the formula:
q i -displacement, velocity, acceleration corresponding to the ith order mode in a regular coordinate system;
ω i -the ratio corresponding to the ith order flexural mode of the structure;
ξ i -equivalent damping ratio corresponding to the ith order compliance mode of the structure;
f i -modal coordinate systemThe load force.
S2, analyzing whether the matching results of the vehicle structure mode and the track structure mode are overlapped or not;
s3, if mode matching generates overlapping, recalculating the rail mode by changing one or more of the rail structure parameters to ensure that the rail structure mode range avoids the vehicle structure mode range; and S2, the structural parameters of the track comprise the length, the width and the height of the track slab, the rigidity of the track slab and the rigidity of a fastener.
If the mode matching is not overlapped, a vehicle-track rigid-flexible coupling dynamic performance analysis model is constructed, dynamic simulation analysis is carried out on the constructed vehicle-track rigid-flexible coupling dynamic performance analysis model, and whether abnormal vibration caused by resonance exists during the running of the vehicle is judged; and (4) establishing a flexible vehicle body, a flexible framework, a flexible wheel set and a flexible track in the vehicle-track rigid-flexible coupling power performance analysis model established in the S3, wherein the flexible track comprises flexible steel rails and a flexible track.
The vehicle-track model is shown in FIG. 2 and known from Dian-Sun Moxing (see Di Wan for vehicle-track coupling dynamics [ M ]. Beijing: scientific Press 2015.). The flexible deformation of the vehicle body, the framework and the wheel set is described by adopting a hybrid coordinate method, and the specific modeling is to disperse finite elements of the vehicle body, the framework and the wheel set. The steel rails are dispersed into space beam units, the track slab is simplified into a space layered viscoelastic body to carry out finite element dispersion (see Ling Liang. Research on high-speed train-track three-dimensional rigid-flexible coupling dynamics [ D ]. Southwest university of transportation 2015.), and a modal superposition method is adopted to solve the flexible vibration response of the train body, the framework, the wheel set, the steel rails and the track slab. The vehicle-track is connected through the wheel track, and the normal force of the wheel track adopts a Hertz nonlinear theoretical model, so that a vehicle-track rigid-flexible coupling dynamic performance analysis model can be finally established. The model can be solved by adopting a Zhai type novel rapid numerical calculation method.
S4, if abnormal vibration exists, returning to the step S2, and re-selecting different track structure parameters to re-calculate the track mode; and S4, different track structure parameters are selected again, the influence factors are unreasonable matching among the track mode, the vehicle distance, the vehicle wheel base and the vehicle mode, specifically unreasonable matching between the track mode and the vehicle mode, unreasonable matching between the track mode and the vehicle distance, unreasonable matching between the track mode and the vehicle wheel base and the like, and the description contents of the vehicle distance and the wheel base in the figure 1 are the consideration factors of resonance caused by the vehicle distance and the vehicle wheel base.
If no abnormal vibration exists, the suppression of the coupling resonance of the vehicle line is successfully realized.
Now, through practical application in engineering, the specific steps of evaluation are shown:
calculating a vehicle structure mode and a track structure mode according to given vehicle and high-speed railway track information, wherein a flexible track schematic diagram and a flexible vehicle body schematic diagram are shown in fig. 3, a low-order mode frequency of a vehicle body, a framework, a wheel pair, a steel rail and a track plate is shown in fig. 4, and whether the matching of the vehicle structure mode and the track structure mode is reasonable or not is analyzed.
As can be seen from fig. 5, since there is an overlapping region between the track slab mode and the vehicle wheel set and between the track slab mode and the vehicle body structure mode frequency at a low level, it is necessary to avoid the overlapping region between the track slab mode and the vehicle structure mode by changing one or more of the length, width, height, rigidity of the track slab, and rigidity of the fastener. After the parameters are changed, the vehicle structure mode and the track structure mode are reasonably matched. And (3) establishing a vehicle-track three-dimensional rigid-flexible coupling dynamic performance analysis model, performing dynamic simulation on the model, wherein the simulation result is shown in fig. 6, the vibration under the normal working condition is referred to in fig. 7, the result shows that abnormal vibration exists when the vehicle runs, and changing the track structure by the method again until the inhibition of the coupling resonance of the train line is successfully realized.
Interpretation of terms:
a modal superposition method: the method is also called as a vibration mode superposition method, and uses the vibration mode (mode) without damping of the system as a space substrate, decouples a motive power equation through coordinate transformation, solves n mutually independent equations to obtain mode displacement, and further obtains the response of the system by superposing the contribution of each order of modes.
The above is only a preferred embodiment of the present invention, and it should be noted that the above preferred embodiment should not be considered as limiting the present invention, and the protection scope of the present invention should be subject to the scope defined by the claims. It will be apparent to those skilled in the art that various modifications and adaptations can be made without departing from the spirit and scope of the invention, and these modifications and adaptations should be considered within the scope of the invention.
Claims (7)
1. A high-speed railway track mode design method for inhibiting train line coupling resonance is characterized by comprising the following operations:
s1, calculating a vehicle structure mode and a track structure mode according to vehicle information and high-speed railway track information:
the vehicle structure mode comprises a vehicle suspension mode, a vehicle body flexibility mode, a framework flexibility mode and a wheel set flexibility mode;
the track structure mode comprises a steel rail flexible mode, a track plate flexible mode and a track integral mode;
the vehicle suspension mode is determined by suspension rigidity, damping and mass properties of a vehicle, the vehicle suspension mode is obtained by establishing a vibration equation of a vehicle system, and a free motion equation of the vehicle system is shown as the formula (1-1):
in the formula: M-N-order quality matrix of the system;
C-N-order damping square matrix of the system;
K-N-order stiffness matrix of the system;
x is generalized displacement of N order;
the characteristic equation of the available vehicle suspension system is shown as the formula (1-2):
|K-ω 2 M|Φ＝0 (1-2)
solving the equation to obtain the natural frequency omega and the natural mode phi of the vehicle;
the flexible mode of the vehicle-track system is determined by the structural shape and the material property, the finite element model of the vehicle body, the framework, the wheel pair, the steel rail and the track plate structure is established by adopting finite element software, the mode analysis is carried out, then the flexible vibration calculation is carried out by adopting a mode superposition method, and the motion equation of the flexible vibration equation of the structure in a floating coordinate system is shown as the formula (1-3):
in the formula:
u f -displacement, velocity, acceleration of flexible vibration of the structure;
M f -a mass matrix of the structure;
C f -a damping matrix of the flexible deformation of the structure;
K f -a stiffness matrix of the flexible deformation of the structure;
F f -a load force acting on the structure;
similarly, according to the mass matrix M of the structure f Stiffness matrix K f The characteristic equation of the structure flexible deformation can be obtained as shown in the formula (1-4):
|K f -ω i 2 M f |ψ f ＝0 (1-4)
wherein: psi f -a structure flexural vibration natural mode;
ω i -a structure flexural vibration natural frequency;
based on the mode superposition principle, the structure flexible vibration is as shown in the formula (1-5):
in the formula: psi f -a modal matrix of the structure;
q f -a modal coordinate vector of the structure;
Ψ fi -a structural body order i modal vector;
q fi -a structure ith order modal coordinate;
so that its vibration equation can be decoupled into a differential equation associated with its front NM order mode as shown in equations (1-6):
in the formula:
q i -displacement, velocity, acceleration corresponding to the ith order mode in a regular coordinate system;
ω i -the ratio corresponding to the ith order flexural mode of the structure;
ξ i -equivalent damping ratio corresponding to the ith order compliance mode of the structure;
f i -a loading force in a modal coordinate system;
s2, analyzing whether the matching results of the vehicle structure mode and the track structure mode are overlapped or not;
s3, if the mode matching generates overlapping, recalculating the track mode by changing one or more of the track structure parameters to ensure that the track structure mode range avoids the vehicle structure mode range;
if the mode matching is not overlapped, constructing a vehicle-track rigid-flexible coupling dynamic performance analysis model: the method comprises the steps of describing flexible deformation of a vehicle body, a framework and a wheel set by adopting a hybrid coordinate method, specifically modeling, dispersing finite elements of the vehicle body, the framework and the wheel set, dispersing steel rails into space beam units, simplifying a track plate into a space layered viscoelastic body, performing finite element dispersion, solving flexible vibration response of the vehicle body, the framework, the wheel set, the steel rails and the track plate by adopting a modal superposition method, establishing connection between a vehicle and a track through a wheel and the track, and adopting a Hertz nonlinear theoretical model for wheel and track normal force so as to finally establish a vehicle-track rigid-flexible coupling dynamic performance analysis model; then carrying out power simulation analysis on the constructed vehicle-track rigid-flexible coupling power performance analysis model, and judging whether abnormal vibration caused by resonance exists during vehicle running;
s4, if abnormal vibration exists, returning to the step S3, and re-selecting different track structure parameters to re-calculate the track mode; if no abnormal vibration exists, the suppression of the coupling resonance of the vehicle line is successfully realized.
2. The method for designing the track mode of the high-speed railway for inhibiting the train line coupling resonance according to claim 1, wherein the vehicle information in the step S1 comprises vehicle suspension system parameters, vehicle body structure parameters, framework structure parameters and wheel pair structure parameters.
3. The high-speed railway track modal design method for inhibiting train line coupling resonance according to claim 1 or 2, wherein the high-speed railway track information in S1 comprises steel rail structure parameters, track slab structure parameters and fastener parameters.
4. The method for designing the track mode of the high-speed railway for inhibiting the train line coupling resonance according to claim 3, wherein the vehicle structure mode in the S1 comprises a vehicle suspension mode, a vehicle body flexibility mode, a framework flexibility mode and a wheel pair flexibility mode, and the track structure mode comprises a steel rail flexibility mode, a track plate flexibility mode and a track integral mode.
5. The high-speed railway track mode design method for inhibiting the train line coupling resonance according to claim 1, wherein the track structure parameters in S3 comprise the length, width and height of the track slab, the rigidity of the track slab and the rigidity of a fastener.
6. The method for designing the track mode of the high-speed railway for inhibiting the train line coupling resonance as claimed in claim 1, wherein the flexible train body, the flexible framework, the flexible wheel pair and the flexible track are built in the vehicle-track rigid-flexible coupling dynamic performance analysis model built in the step S3.
7. The method for designing the track mode of the high-speed railway for inhibiting the train line coupling resonance according to claim 1, wherein different track structure parameters are reselected in the step S3, and the influence factors are unreasonable matching among the track mode, the vehicle distance, the vehicle wheel base and the vehicle mode.
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